WO2009015632A1 - Dispositif pour amortir des vibrations, en particulier amortisseur de vibrations torsionnelles à plusieurs étages - Google Patents

Dispositif pour amortir des vibrations, en particulier amortisseur de vibrations torsionnelles à plusieurs étages Download PDF

Info

Publication number
WO2009015632A1
WO2009015632A1 PCT/DE2008/001146 DE2008001146W WO2009015632A1 WO 2009015632 A1 WO2009015632 A1 WO 2009015632A1 DE 2008001146 W DE2008001146 W DE 2008001146W WO 2009015632 A1 WO2009015632 A1 WO 2009015632A1
Authority
WO
WIPO (PCT)
Prior art keywords
damper
damper assembly
output part
flange
series
Prior art date
Application number
PCT/DE2008/001146
Other languages
German (de)
English (en)
Inventor
Stephan Maienschein
Original Assignee
Luk Lamellen Und Kupplungsbau Beteiligungs Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Luk Lamellen Und Kupplungsbau Beteiligungs Kg filed Critical Luk Lamellen Und Kupplungsbau Beteiligungs Kg
Priority to DE112008001861T priority Critical patent/DE112008001861A5/de
Publication of WO2009015632A1 publication Critical patent/WO2009015632A1/fr
Priority to US12/697,579 priority patent/US8047922B2/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F16F15/12353—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
    • F16F15/1236—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates
    • F16F15/12366—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs

Definitions

  • the invention relates to a device for damping vibrations, in particular a multi-stage torsional vibration damper, comprising at least two coaxially arranged and at least one input part and one output part having and arranged on different diameters damper assemblies - a first radially outer damper assembly, which as a series damper, comprising at least two series connected and coupled via an intermediate flange damper is formed and a second radially inner damper assembly.
  • a device for damping vibrations in particular a multi-stage torsional vibration damper, comprising at least two coaxially arranged and at least one input part and one output part having and arranged on different diameters damper assemblies - a first radially outer damper assembly, which as a series damper, comprising at least two series connected and coupled via an intermediate flange damper is formed and a second radially inner damper assembly.
  • Mechanical dampers comprise a one- or multi-part, depending on the direction of force flow acting as an input part or output part of the device for damping vibrations rotating part, in particular a primary part and a secondary part, which are arranged coaxially to one another and in the circumferential direction are limited rotatable relative to each other.
  • the coupling between the input part and the output part via means for transmitting torque and means for damping vibrations, which are usually formed by spring units comprising at least one spring element in the form of a compression spring.
  • spring units comprising at least one spring element in the form of a compression spring.
  • the document US 2004/0216979 A1 discloses an embodiment of a device for damping vibrations, comprising at least two damper arrangements, which are connected in parallel, both damper arrangements always being effective.
  • the damper arrangement for the smaller angle of rotation is here arranged on a radially inner diameter, while the larger torsional backlash is realized on the second damper arrangement on a radially outer diameter.
  • the radially inner damper assembly is designed as a series damper, comprising via a one-piece flange separated and successively connected spring elements.
  • a device designed as a series-parallel damper for damping vibrations comprising a first rotary element and a second rotary element, which are rotatable relative to each other in the circumferential direction. Furthermore, the device comprises a pair of first, aligned in one direction and in series elastic elements, which are coupled via a floating intermediate flange, and a further second elastic element, which is connected in parallel to the first elastic elements, wherein the second elastic element is configured to be compressed in the rotational direction after the pair of first elastic elements has been compressed to a first angle due to relative rotation of the first rotary member and the second rotary member.
  • the second elastic element is assigned to a clearance angle, which is integrated in the floating flange.
  • first and second elastic elements are carried out to reduce the radial space on a diameter or in the radial direction with respect the annular areas theoretically resulting from the extension of the spring elements overlap each other.
  • the coupling between the first elastic elements via a floating flange.
  • the separation of the spring units into row damper assemblies forming the radially outer damper stage is generally accomplished by a floating flange.
  • This is provided as an annular element with projections formed on the inner circumference, which forms a contact surface in the central region for the spring units.
  • the intermediate flange often proves to be stress and deformation critical under loads.
  • a series damper device is previously known from the document US 3,138,011.
  • the damper described therein has two arranged on different diameters damper stages, wherein the first is designed as a series damper with arranged on a diameter means for torque transmission and damping coupling.
  • the device further comprises two side plates and an interposed, acting as the output flange annular flange and floating between the annular flange and side plates and provided with openings for spring elements discs which separate the spring units of each damper of the series damper.
  • the invention is therefore an object of the invention to provide a device for damping vibrations with an intermediate flange separated damper a series damper assembly, in which the intermediate flange should be characterized by a low-voltage design.
  • the solution according to the invention should be characterized by a low design and manufacturing effort and also be suitable for integration in power transmission devices for use in drive trains, the device should build small for damping vibrations as possible in the radial and axial directions.
  • the solution according to the invention is characterized in that the intermediate flange consists of at least two spaced apart in the axial direction and on both sides of the output part of the first damper assembly extending at least into the region of the outer circumference of the output part of the first damper assembly annular disk-shaped elements, each comprising in the circumferential direction extending openings.
  • the inventive at least two-part design of the intermediate flange in the form of annular disk-shaped elements with closed in the region of the inner periphery edge offers over the one-piece open design the advantage of lower voltages under load and a smaller material thickness, which has a reduction of the mass moment of inertia result. This reduction contributes to the shifting of the resonance of the intermediate flange in speed-less critical areas. Remaining vibrations at a lower energy level can be damped according to a further development by an additional friction device. This can be generated by elastic elements which are arranged between the annular disk-shaped elements and press them in the axial direction against the side windows.
  • the device for damping vibrations is designed as a series-parallel damper, comprising two parallel damper stages, which are arranged on different diameters, wherein the second is carried out with torsional backlash.
  • the arrangement of the first damper assembly is carried out according to the invention on a diameter in the radial direction, which is greater than the diameter of the arrangement of the second damper assembly.
  • Output part of the first damper assembly and output part of the second damper assembly form a structural unit.
  • the production is relatively simple and associated with low costs due to the functional concentration in individual components.
  • the second damper assembly is arranged as possible at a small distance from the axis of rotation. Both damper assemblies are arranged coaxially with each other and can be arranged in the axial direction with offset or preferably in a plane. In the latter case, the damper assembly in the form of the multi-stage damper, in which the damper characteristic can be set variably due to the separate configuration of the individual damper assembly, relatively small in the axial direction and radial direction.
  • the first damper assembly comprises at least two series-connected damper, a first and a second damper, wherein in each case the output part of a damper forms the input part of the other damper or non-rotatably coupled thereto.
  • the series damper is realized on a common diameter, that is, the two individual dampers are arranged on a common diameter and free of offset in the radial direction. In this case, the radial dimensions for the overall damper can be kept low.
  • Each of the individual damper arrangements viewed in the direction of force flow, comprises a primary part acting as an input part and a secondary part functioning as an output part.
  • the function is interchangeable depending on the direction of force flow and change, that is, changes.
  • the input and output parts can be formed in one or more parts.
  • each one-piece designs are selected in disc form.
  • the means for torque transmission and for damping coupling are formed by elastic elements, in particular spring units.
  • the individual spring units are designed as a single spring or can also be present as a series connected spring units.
  • the single damper assembly acts as a flexible coupling that transmits torque and at the same time compensates for vibrations.
  • the first damper arrangement comprises at least both an input part and an output part.
  • the same applies to the second damper arrangement wherein, however, the input part of the first and the second damper arrangement are coupled to each other or connected in parallel, so that here a torque distribution can take place via the two damper arrangements.
  • a structural unit ie, for example, can be coupled together rotationally fixed.
  • the individual input and output parts are designed as separate elements, which are functionally coupled to each other only via the connection.
  • an integral construction that is, input part and output part of the first and second damper assembly are each made in one piece, that is, the input part or output part forming elements of the first damper assembly are simultaneously as an input part or output part of the second damper assembly executed.
  • Each of the individual dampers of a series damper arrangement of the first damper stage has for this purpose preferably identically dimensioned means for transmitting torque and / or means for damping coupling.
  • the individual dampers of the first damper arrangement can be designed differently.
  • the individual dampers of the first damper arrangement designed as a series damper are coupled to one another via the two-part or multi-part intermediate flange design, which can be designed as a drive plate or as a floating flange, depending on the connection.
  • the torsional backlash of the second damper arrangement is characterized by a predefined angle of rotation describing a clearance angle between the input part and the output part of the second damper arrangement, in which the second damper arrangement is not effective.
  • the twist angle is integrated in the output part.
  • the device is designed as a mechanical friction damper.
  • this comprises at least two side windows, which are arranged in the axial direction and are non-rotatably coupled to one another and which can function as driver disks or as an output part.
  • the side windows comprise openings formed in the circumferential direction for receiving and Training of mutually oppositely shaped abutment surfaces for the spring elements of the individual damper assemblies and the damper of the first damper assembly.
  • the abutment surfaces in the circumferential direction forming recesses or through holes are arranged to each other such that for the second damper assembly, a clearance angle, that is a VerF Scheme between input and output part can be realized, which shows no effect with respect to the second damper device, that is, the second Damper device only becomes effective when a certain predefined angle of rotation between the input part and the output part is achieved.
  • this statement also applies to the arranged between the two side windows flange, in particular the disc-shaped element in the form of the flange, which also forms the output part of the first and the second damper assembly.
  • the different elements can each act as an input part. This depends on which of the elements are coupled to the drive assembly and which is viewed with the output side in the direction of power flow.
  • the drive can be realized via side windows. In this case, these are non-rotatably coupled to a driving element, for example in a power transmission device of a lock-up clutch or a drive machine, at least indirectly.
  • the power transmission then takes place in the first damper assembly on the intermediate flange and from there to the flange, which forms the output part of the device and the output part of the second damper assembly.
  • Figure 1a illustrates in a schematic simplified representation of the basic structure and the basic principle of a device according to the invention for damping vibrations in the form of a series-parallel damper in a view from the right;
  • Figures 1 b and 1c illustrate in a schematic simplified representation of two axial sections according to A-A and B-B according to Figure 1a of a device according to the invention for damping vibrations;
  • Figure 1d illustrates a view according to Figure 1a free from the axial side windows
  • Figure 2 illustrates an intermediate flange and an output flange in a perspective view.
  • Figures 1a to 1d illustrate in a schematic simplified representation of the basic structure and the basic principle of an inventively designed device 1 for damping vibrations, in particular in the form of a torsional vibration damper or Torsionsschwingungsdämpfers in several views.
  • Figure 1a illustrates in a simplified schematic representation of the basic structure and the basic principle of a device according to the invention for damping vibrations in the form of a series-parallel damper in a view from the right.
  • Figures 1b and 1c illustrate in a schematic simplified representation of two axial sections according to AA and BB according to Figure 1a and Figure 1d illustrates a view according to Figure 1a free from the axial side windows.
  • Figure 1a illustrates in a schematic simplified representation of the basic structure and the basic principle of an inventively designed device 1 for damping vibrations, in particular in the form of a torsional vibration damper or Torsionsschwingungsdämpfers in several views.
  • Figure 1a illustrates in a simplified schematic representation of the
  • the inventive device 1 for damping vibrations is designed as a multi-stage series-parallel damper 2.
  • the device 1 for damping vibrations comprises functionally two damper stages 3, 4, which are each formed by a damper arrangement - a first damper assembly 5 and a second damper assembly 7 - and are connected in parallel.
  • Parallel connected means that both damper assemblies 5 and 7 are arranged in parallel in the power flow.
  • the power flow takes place in parallel or via both damper arrangements 5 and 7.
  • the first damper arrangement 5 is arranged outside in the radial direction and designed as a series damper, that is, comprises at least two series-connected dampers 6.1 and 6.2.
  • both dampers 6.1 and 6.2 in the damper stage 3 are passed through in succession, the direction being determined as a function of the force introduction direction. Both are attached to a diameter d 3 . which is larger than the diameter d 4 of the second radially inner damper stage 4. Both damper 6.1 and 6.2 are coupled via an intermediate flange 23 with each other.
  • the intermediate flange 23 is inventively not one piece but executed in several parts. This comprises two floating annular disk-shaped elements 23.1, 23.2, which are arranged next to each other in the axial direction spaced apart. These extend in the radial direction with their inner diameter into a region which extends into the region of the outer circumference of the output part of the first damper arrangement 5.
  • each of the damper stages 3 and 4 is effective in different operating ranges.
  • the damper assembly 7 of the second damper stage 4 is designed such that it only after a predefined angle of rotation F, which is also referred to as clearance angle, is effective.
  • Both damper assemblies 5 and 7 are arranged in parallel and combined into a two-stage series-parallel damper.
  • Each of the individual damper arrangements 5 and 7 comprises one-part or multi-part rotary elements which act as input parts and output parts in the direction of flow of force and which are coupled to one another via means for torque transmission and / or means for damping coupling.
  • the means for transmitting torque and the means for damping coupling are formed by the same structural units, preferably spring units.
  • the input and output parts of the individual damper assemblies 5, 7 and the individual damper 6.1, 6.2 of the damper assembly 5 are each arranged coaxially to one another and limited in the circumferential direction against each other rotatable.
  • the term input and output part refers to the force flow when viewed in the direction of force flow when arranged in a drive train from a driving to a driven component.
  • the functions as input and output part can be assigned to different components in different operating states, that is, when used in vehicles in drive trains in traction operation elements that can be coupled to a prime mover, as the input part, while in overrun a function reversal by the element acting as the output part in the traction mode now functions as an input part.
  • the input device E is formed by an element of the damper assembly 5 and the damper assembly 7 as a structural unit or the input parts of the damper assemblies 5 and 7 are rotatably connected to each other.
  • the damper arrangement 5 comprises an input part 8 and an output part 10.
  • the damper arrangement 7 comprises an input part 11 and an output part 12.
  • the input parts 8 and 11 are present here. formed directly from the input part E and the output parts 10, 12 from the output part A.
  • two dampers are connected in series, the damper 6.1 and the damper 6.2.
  • the input 8 of the first damper assembly which is non-rotatably connected to the input E of the entire unit or preferably formed directly from this, is formed by the input part 13 of the first damper 6.1.
  • the first damper 6.1 further comprises an output part 14, which simultaneously forms the input part 15 of the second damper 6.2 of the two series-connected damper of the damper assembly 5, here the intermediate flange 23, in particular the two annular disk-shaped elements 23.1, 23.2.
  • the second damper 6.2 further comprises an output part 16 which forms the output part 10 of the damper assembly 5 and which is non-rotatably connected to the output A or forms this.
  • the first damper 6.1 comprises means 17 for transmitting torque between the input part 13 and the output part 14 and means 18 for damping coupling.
  • the second damper 6.2 comprises means 20 for torque transmission and means 21 for damping coupling.
  • the inner periphery 28 of the annular disk-shaped elements 23.1, 23.2 can be described by a diameter which is smaller than the outer diameter of the output part 10 of the first damper assembly. That is, the annular disk-shaped elements 23.1, 23.2 are on both sides of the output part 10 or enclose this in the region of its outer periphery.
  • the second damper arrangement 7 comprises at least one damper, in which the input part 11 and the output part 12 are coupled to one another via means 34 for torque transmission and means 35 for damping coupling.
  • the power flow takes place between the input part E and the output part A of the device depending on the direction of rotation in the first damping assembly 5 via the damper 6.1 and the damper 6.2 or vice versa and simultaneously after reaching the predefined angle of rotation between input part E and output part A, the damper assembly. 7
  • the arrangement of the first damper stage 3 takes place in the radial direction with respect to the rotation axis R of the device 1 to a larger diameter d3 than the second further damper stage 4 to d 4th
  • the arrangement of the first damper assembly 5 is radially outward
  • the arrangement of the second damper assembly 7 is within the extension of the inner diameter of the first damper assembly 5 and thus on a smaller diameter d 4 .
  • the input part E of the device 1 and thus the input parts 8, 10 of the damper assemblies 5, 7 are spaced apart from each other and arranged coaxially with each other formed Mit videimin 9.1 and 9.2, which are rotatably coupled together.
  • the first damper assembly 5 consists of the two dampers 6.1 and 6.2.
  • the input part 13 of the first damper 6.1 is formed by the drive plates 9.1 and 9.2. This applies analogously to the input part 11 of the second damper assembly 7, wherein the input part 11 is also formed here by the Mit lecturusionn 9.1 and 9.2.
  • the first damper 6.1 comprises means 17 for torque transmission between the input part 13 and the output part 14 and means 18 for damping coupling, in which case the means 17 and the means 18 of a structural unit, in particular a spring unit 19, comprising at least one spring element in the form of a compression spring become.
  • the second damper 6.2 also includes means 20 for torque transmission and means 21 for damping coupling, these being formed by a further spring unit 22.
  • the input part 13 is, as already stated, formed by the Mit videmin 9.1 and 9.2, the output part 14 of a so-called floating intermediate flange 23 of the two annular disk-shaped elements 23.1, 23.2, which are free of a coupling with each other and free of its own storage or non-rotatable connection to a connection element.
  • the intermediate flange 23 forms the input part 15 of the second damper 6.2.
  • the output part 16 of the second damper 6.2 and thus the output part 10 and A of the device 1 is formed by a flange 24.
  • the means 17 and 18 or the individual spring units 19 of the first damper 6.1 are based in the drive plates 9.1 and 9.2, the flange 24 or the intermediate flange 23, while the spring units 22 of the second damper 6.2 also on the drive plates 9.1, 9.2 or the Can support flange 23 and the flange 24 in the circumferential direction.
  • the intermediate flange 23 and the annular disk-shaped elements 23.1, 23.2 forming this are designed as floating flange, that is, this has no own storage and is only by the spring units 19, 22 and the arrangement of the flange 24 and the side windows 9.1 and 9.2 between the spring units 19, 22 held.
  • the openings 25 in the intermediate flange 23 and the individual annular disk-shaped elements 23.1, 23.2 form circumferentially aligned and oppositely directed abutment surfaces 26 and 27 for the spring units 19 and 22 of the damper 6.1 and 6.2.
  • the flange 24 shown in FIG. 1d in a side view here forms the output part 10, 12 of both the first and the second damper arrangement 5, 7 and thus also the output part A of the entire apparatus 1 for damping vibrations. This is designed for this purpose as a disk-shaped element.
  • the flange 24, which forms the output part 10 and 12 of the damper assemblies 5, 7, is designed as a radially inner flange and has at its outer periphery 29 in the radial direction outwards, that is away from the axis of rotation R away and in the circumferential direction at a uniform distance mutually arranged projections 30, wherein two adjacent projections 30 circumferentially extending open-edge recesses describe in which the two spring units 19 and 22 of the individual dampers 6.1 and 6.2 are arranged and at the opposite side surfaces 31 and 32 of such a recess on Support flange 24.
  • the flange 24 includes on its diameter d 4 further recesses 33 in the form of circumferentially extending openings which support surfaces 37.1, 37.2 for the spring units 36 of the means 34 for torque transmission or 35 for damping coupling.
  • the support surfaces 37.1, 37.2 are arranged opposite each other in the circumferential direction. However, these support surfaces 37.1, 37.2 become effective only after a certain angle of rotation F.
  • the spring units 36 are supported on the side windows 9.1 and 9.2 and the flange 24.
  • the figure 1a illustrates in a schematic simplified representation of a side view of the side windows in the form of driving plates 9.1 and 9.2 of the device 1. Also recognizable here is a disc-shaped configuration in the form of an annular disc with openings formed in the circumferential direction 41 for receiving the spring units 19 and 22 of the damper 6.1 and 6.2 and supports in the circumferential direction and radial direction.
  • the driver disks have openings 42 for the second damper arrangement 7, which are arranged on a smaller diameter and receive the spring units 36.
  • a moment is introduced into the damper assembly 5 in the direction of power flow when used in drive trains and vehicles in the normal traction of the prime mover to a downstream power transmission unit via the Mit Meetingusionn 9.1 and 9.2, which are rotatably coupled to each other, according to Figure 1d depending on Direction of rotation, the spring units 19 or 22 are acted upon, in turn, act on the intermediate flange 23, in particular the projection 25 via the stop surfaces 26 and 27 and due to the consequent coupling the torque transmission while damping coupling via the intermediate flange 23 to the other spring unit, here, for example Spring unit 22, and from this on the flange 24, which forms the output part A, cause.
  • the second damper stage 4 If a relative rotation between the drive plates 9.1, 9.2 and the flange 24 in size of the clearance angle F, the second damper stage 4 is effective. After reaching this clearance angle F, the power transmission takes place in addition via the second damper stage 4 also acting as the output part A of the overall device output 12 of the second damper stage 4.
  • the individual spring units 19, 22, 36 are executed here, for example in the form of so-called compression springs or as coil springs. Other versions of elastic elements are also theoretically conceivable.
  • fasteners 38 are provided, preferably in the form of rivets. These can lie radially outside the radial extent of the spring units 19, 22 of the damper stage 3 and between intermediate flange elements 23.1, 23.2 and flange 24, as shown in FIG. 1d. Furthermore, the arrangement can be made radially outside the outer diameter of the intermediate flange 23.
  • the non-rotatable coupling can simultaneously form a stop in the circumferential direction and thus a Vermoswinkelbegrenzung for the intermediate flange 23 and the flange 24.
  • FIGS. 1 a and 1 d furthermore illustrate an arrangement of the individual damper stages 3 and 4 in an axial plane, which is particularly related to the design of the output part 10 functioning as output part A of the device 1.
  • approximately 12 of the two damper assemblies 5 and 7 is realized. This is, as already stated, formed in the simplest case as a disk-shaped element.
  • the projections 30 on the outer circumference 29 of the flange 24 also have abutment surfaces 39.1, 39.2 which cooperate with correspondingly formed on the inner circumference 28 of the intermediate flange 23 and circumferentially opposite to the abutment surfaces 39.1, 39.2 aligned stop surfaces 40.1, 40.2. These form a block protection for the spring units 19, 22 in the first damper stage 3.
  • the stop surfaces 39.1, 39.2, 40.1, 40.2 are therefore arranged such that they form only a Verwarwinkelbegrenzung between the intermediate flange 23 and flange 24 at a certain predefined travel.
  • FIG. 1 illustrates a particularly compact device suitable for use in power transmission devices for vehicles, comprising a hydrodynamic component and a bypass device for the hydrodynamic component, which device is arranged in series with the hydrodynamic component as well as with the bridging device.
  • FIG. 2 illustrates, in a perspective view, the formation of the intermediate flanges 23 and of the flange 24 in the installed position. Visible are the two annular disk-shaped elements 23.1, 23.2, which are spaced from each other and extending therebetween flange 24.
  • the individual annular disk-shaped elements 23.1, 23.2 viewed in cross section must not be designed plan, but can, especially in the Umsch originallyungs Scheme on the outer periphery 29 of the flange 24 be executed slightly cranked.
  • the embodiment according to the invention according to FIGS. 1 and 2 is characterized by a high degree of functional concentration, high compactness and at the same time a low number of components. Furthermore, it is possible with this embodiment to design a torsional vibration damper with the lowest possible spring rate, which has the largest possible angle of rotation with low friction. This is also realized in that preferably the series damper assembly is arranged on the larger diameter.

Abstract

L'invention concerne un dispositif (1) servant à amortir des vibrations, en particulier un amortisseur à plusieurs étages, comprenant au moins deux agencements d'amortissement (5, 7) disposés coaxialement qui présentent chacun au moins une pièce d'entrée (8, 11) et une pièce de sortie (10, 12) et sont disposés sur des diamètres différents, à savoir un premier agencement d'amortissement (5) extérieur dans le sens radial se présentant sous la forme d'un amortisseur en série comprenant au moins deux amortisseurs (6.1, 6.2) montés en série et couplés par une bride intermédiaire (23) et un deuxième agencement d'amortissement (7) intérieur dans le sens radial. L'invention se caractérise en ce que la bride intermédiaire (23) se compose d'au moins deux éléments en forme de disque annulaire espacés dans le sens axial et s'étendant de chaque côté de la pièce de sortie (12) du premier agencement d'amortissement (5) au moins dans la région de la périphérie extérieure (29) de ladite pièce de sortie (12), ces éléments comprenant chacun des ouvertures (25) s'étendant dans le sens périphérique.
PCT/DE2008/001146 2007-08-02 2008-07-10 Dispositif pour amortir des vibrations, en particulier amortisseur de vibrations torsionnelles à plusieurs étages WO2009015632A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112008001861T DE112008001861A5 (de) 2007-08-02 2008-07-10 Vorrichtung zur Dämpfung von Schwingungen, insbesondere einen mehrstufigen Drehschwingungsdämpfer
US12/697,579 US8047922B2 (en) 2007-08-02 2010-02-01 Vibration damper, particularly a multistage torsion vibration damper

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007036190 2007-08-02
DE102007036190.6 2007-08-02

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US12/697,579 Continuation US8047922B2 (en) 2007-08-02 2010-02-01 Vibration damper, particularly a multistage torsion vibration damper

Publications (1)

Publication Number Publication Date
WO2009015632A1 true WO2009015632A1 (fr) 2009-02-05

Family

ID=39873966

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2008/001146 WO2009015632A1 (fr) 2007-08-02 2008-07-10 Dispositif pour amortir des vibrations, en particulier amortisseur de vibrations torsionnelles à plusieurs étages

Country Status (3)

Country Link
US (1) US8047922B2 (fr)
DE (2) DE102008032459A1 (fr)
WO (1) WO2009015632A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2960613A1 (fr) * 2010-06-01 2011-12-02 Valeo Embrayages Dispositif d'amortissement angulaire equipe de moyens de frottement variables en fonction de la vitesse de rotation.

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2947025B1 (fr) 2009-06-18 2011-07-15 Valeo Embrayages Amortisseur, notamment pour un dispositif de couplage en rotation de vehicule automobile
DE102010053934B4 (de) 2009-12-21 2022-10-06 Schaeffler Technologies AG & Co. KG Vorrichtung zur Dämpfung von Schwingungen
WO2011110151A2 (fr) * 2010-03-11 2011-09-15 Schaeffler Technologies Gmbh & Co. Kg Flasque de transmission pour un dispositif de transmission de couple ou un dispositif d'amortissement, ainsi que dispositif de transmission de couple ou un dispositif d'amortissement
WO2011157257A1 (fr) * 2010-06-17 2011-12-22 Schaeffler Technologies Gmbh & Co. Kg Dispositif d'amortissement d'oscillations
FR2969730B1 (fr) 2010-12-23 2014-02-21 Valeo Embrayages Organe de phasage pour un amortisseur de torsion
JP5589883B2 (ja) 2011-02-15 2014-09-17 アイシン・エィ・ダブリュ株式会社 ダンパ装置
FR2974871B1 (fr) 2011-05-04 2013-05-17 Valeo Embrayages Dispositif d'amortissement de torsion comportant des organes elastiques dont chacun est maintenu individuellement en position par une rondelle de phasage
FR2988455B1 (fr) 2012-03-20 2014-03-14 Valeo Embrayages Dispositif de transmission de couple pour un vehicule automobile
JP6185827B2 (ja) * 2013-11-28 2017-08-23 株式会社エフ・シー・シー ロックアップ装置およびトルクコンバータ
DE112015001231T5 (de) * 2014-03-13 2016-12-15 Schaeffler Technologies AG & Co. KG Federhalterungsscheibe mit ausgeschnittenen Federanschlägen
JP6252458B2 (ja) 2014-04-30 2017-12-27 アイシン・エィ・ダブリュ株式会社 ダンパ装置
FR3039235B1 (fr) 2015-07-24 2019-04-12 Valeo Embrayages Dispositif d’amortissement de vibration
FR3039237B1 (fr) 2015-07-24 2018-03-02 Valeo Embrayages Dispositif de transmission de couple pour un vehicule automobile
JP7154696B2 (ja) * 2018-08-08 2022-10-18 ジヤトコ株式会社 ダンパ装置
CN218670401U (zh) 2019-12-25 2023-03-21 法雷奥汽车工业和商业股份公司 振动阻尼装置

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3138011A (en) * 1962-08-17 1964-06-23 Borg Warner Vibration damper assembly
DE3047039A1 (de) * 1979-12-26 1981-09-03 Borg-Warner Corp., 60604 Chicago, Ill. Zweistufiger drehschwingungsdaempfer
DE19642913A1 (de) * 1995-10-20 1997-04-24 Exedy Corp Dämpfungsscheibenanordnung
DE19652730A1 (de) * 1995-12-22 1997-06-26 Luk Lamellen & Kupplungsbau Triebscheibe
EP1460303A1 (fr) * 2003-03-20 2004-09-22 ZF Sachs AG Amortisseur de vibrations de torsion
US20040185940A1 (en) * 2003-03-18 2004-09-23 Kozo Yamamoto Damper mechanism and damper disk assembly
US20040216979A1 (en) * 2003-03-07 2004-11-04 Toyota Jidosha Kabushiki Kaisha Damper device and lock-up clutch device

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4789375A (en) * 1986-12-16 1988-12-06 Dana Corporation Spring damper drive for a clutch driven disc assembly
FR2764661B1 (fr) * 1997-06-17 1999-09-10 Valeo Amortisseur de torsion pour embrayage de verrouillage appartenant a un appareil d'accouplement hydrocinetique, notamment pour vehicule automobile

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3138011A (en) * 1962-08-17 1964-06-23 Borg Warner Vibration damper assembly
DE3047039A1 (de) * 1979-12-26 1981-09-03 Borg-Warner Corp., 60604 Chicago, Ill. Zweistufiger drehschwingungsdaempfer
DE19642913A1 (de) * 1995-10-20 1997-04-24 Exedy Corp Dämpfungsscheibenanordnung
DE19652730A1 (de) * 1995-12-22 1997-06-26 Luk Lamellen & Kupplungsbau Triebscheibe
US20040216979A1 (en) * 2003-03-07 2004-11-04 Toyota Jidosha Kabushiki Kaisha Damper device and lock-up clutch device
US20040185940A1 (en) * 2003-03-18 2004-09-23 Kozo Yamamoto Damper mechanism and damper disk assembly
EP1460303A1 (fr) * 2003-03-20 2004-09-22 ZF Sachs AG Amortisseur de vibrations de torsion

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2960613A1 (fr) * 2010-06-01 2011-12-02 Valeo Embrayages Dispositif d'amortissement angulaire equipe de moyens de frottement variables en fonction de la vitesse de rotation.
WO2011151570A1 (fr) * 2010-06-01 2011-12-08 Valeo Embrayages Dispositif d'amortissement angulaire equipe de moyens de frottement variables en fonction de la vitesse de rotation
US8795092B2 (en) 2010-06-01 2014-08-05 Valeo Embrayages Angular damping device fitted with friction means variable according to rotation speed

Also Published As

Publication number Publication date
DE102008032459A1 (de) 2009-02-05
US8047922B2 (en) 2011-11-01
US20100133062A1 (en) 2010-06-03
DE112008001861A5 (de) 2010-04-22

Similar Documents

Publication Publication Date Title
EP2176566B1 (fr) Dispositif de transmission de puissance comprenant un composant hydrodynamique et un embrayage de verrouillage et un dispositif pour amortir les vibrations
WO2009015632A1 (fr) Dispositif pour amortir des vibrations, en particulier amortisseur de vibrations torsionnelles à plusieurs étages
DE112008003168B4 (de) Kraftübertragungsvorrichtung, insbesondere zur Leistungsübertragung zwischen einer Antriebsmaschine und einem Abtrieb
EP0304474B1 (fr) Accouplement elastique
WO2009018794A2 (fr) Dispositif d'amortissement de vibrations, en particulier amortisseur de vibrations de torsion à étages multiples
WO2009146673A1 (fr) Amortisseur de vibrations de torsion avec pendule à force centrifuge
EP1945968A2 (fr) Amortisseur en rangee-parallele a plusieurs etages pour convertisseur de couple
DE102010054249B4 (de) Kraftübertragungsvorrichtung
DE102007057431B4 (de) Hydrodynamische Kopplungseinrichtung
DE112014004011T5 (de) Dämpfungsscheibenanordnung
DE112014005023T5 (de) Schwungradanordnung
DE112015000562T5 (de) Dämpfungsscheibenanordnung
DE112011101594B4 (de) Dämpfungsmechanismus
DE112015002003T5 (de) Hydrokinetische Drehmomentkupplungsvorrichtung mit zentrierter Überbrückungskupplungsreibscheibe und Verfahren zu deren Montage
DE602006000393T2 (de) Reibungskupplung, insbesondere für Kraftfahrzeug, mit verbesserten Federscheiben
DE102008043781A1 (de) Torsionsschwingungsdämpfer für den Antriebsstrang eines Fahrzeugs
DE102005055795A1 (de) Leistungsübertragungseinheit
DE112013002693T5 (de) Schwungradanordnung
EP1584838B1 (fr) Amortisseur de vibrations de torsion
DE102016011904A1 (de) Doppelkupplungseinrichtung
DE102021117393A1 (de) Dämpfungsvorrichtung
DE102008005023A1 (de) Kraftübertragungsvorrichtung
WO2008077376A2 (fr) Dispositif de transmission de force
DE10022628C1 (de) Vorrichtung zur Dämpfung von Schwingungen, insbesondere Torsionsschwingungsdämpfer
DE102007057432A1 (de) Hydrodynamische Kopplungseinrichtung

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 08784330

Country of ref document: EP

Kind code of ref document: A1

REF Corresponds to

Ref document number: 112008001861

Country of ref document: DE

Date of ref document: 20100422

Kind code of ref document: P

122 Ep: pct application non-entry in european phase

Ref document number: 08784330

Country of ref document: EP

Kind code of ref document: A1